JP2012096743A - Vibration reducing structure of vehicle seat - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide the vibration reducing structure of a vehicle seat which structure reduces vibrations generated at a seat in accordance with a wide range of frequencies of vibrations.SOLUTION: The vibration reducing structure 1 of the vehicle seat includes a rocking member 2 having a support 21a supported rockably by a seat back frame 10 of the vehicle seat, and a slide member 3 which is fixed to the seat back frame 10 and slides along the rocking member 2 to generate a friction.

Description

  The present invention relates to a vibration reduction structure that reduces vibration of a vehicle seat.

Conventionally, in order to reduce resonance of a vehicle seat due to, for example, input of vibration from a road surface during traveling, a dynamic damper is attached to the vehicle seat.
For example, Patent Document 1 discloses a dynamic damper in which a metal damper mass is supported from above and below by an elastic member on a frame (seat back frame) of a backrest portion of a vehicle seat.
In this dynamic damper, the weight of the damper mass and the spring constant of the elastic member are tuned so as to absorb vibration corresponding to the resonance frequency of the vehicle seat.

JP 2004-116654 A

  However, the dynamic damper described in Patent Document 1 absorbs only vibrations of a specific frequency using an elastic member that matches the natural frequency of the vehicle seat, and can be applied to various vehicle seats generated in the vehicle. It was difficult to absorb a wide range of vibrations.

  The present invention has been made in view of these problems, and an object of the present invention is to provide a vibration reduction structure for a vehicle seat that can reduce vibration generated in the seat corresponding to a wide range of frequencies.

  The present invention provides a vibration reducing structure for a vehicle seat, the swing member having a support portion swingably supported by the frame member of the vehicle seat, and the swing member fixed to the frame member. And a sliding member that generates friction by sliding.

  According to this configuration, when vibration is input to the vehicle seat, the swinging member that is swingably supported by the frame member swings relative to the sliding member that is fixed to the frame member. . As a result, the oscillating member and the sliding member slide to generate friction between them, and the vibration energy is absorbed. Thereby, even if vibrations other than a specific frequency are input and the vehicle seat vibrates, the vibrations can be suppressed by friction.

  Further, it is preferable that the frame member is a seat back frame, and the swinging member is installed on an occupant side seated on the vehicle seat with respect to the sliding member.

  According to this configuration, the frame member is the seat back frame, and the swinging member is installed on the occupant side seated on the vehicle seat with respect to the sliding member, so that the occupant can sit on the vehicle seat. Then, when the seat back frame is inclined to the side opposite to the occupant, the swinging member comes into contact with the sliding member due to gravity, and friction is generated. Therefore, it is possible to omit a pressing mechanism that makes the swinging member contact the sliding member.

  The swing member includes a plate portion provided with the support portion on one end side, and a mass portion provided on the other end side of the plate portion and having a mass larger than that of the plate portion, The sliding member is preferably arranged between the support part and the mass part.

  According to such a configuration, the sliding member comes into contact with a position having a smaller amplitude than the portion where the mass portion is disposed (a position close to the support portion), so that the sliding member can be reduced in size.

  Further, it is preferable that a pressing mechanism that presses the swing member toward the sliding member is further provided, and the pressing mechanism is provided between the support portion and the sliding member.

  According to such a configuration, the pressing mechanism presses a position closer to the support portion than the sliding member, so that the pressing mechanism can be reduced in size.

  ADVANTAGE OF THE INVENTION According to this invention, the vibration reduction structure of the vehicle seat which can reduce the vibration which generate | occur | produces in a sheet | seat corresponding to a wide frequency can be provided.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a structural diagram of a seat back frame including a vehicle seat vibration reducing structure according to a first embodiment, where (a) is a front view and (b) is a side view. It is a graph which shows a time-dependent change of the vibration acceleration in a seat back frame, (a) is the comparative example 1 which does not provide a vibration reduction structure, (b) is Example 1 which adjusted the friction of the vibration reduction structure appropriately, (c) ) Shows a comparative example 2 in which the friction of the vibration reducing structure is stronger than that of the first embodiment. It is a graph which shows the relationship between the frequency in a seat back frame, and a response sensitivity. It is structural drawing of a seat back frame provided with the vibration reduction structure of the vehicle seat which concerns on 2nd Embodiment, (a) is a front view, (b) is a side view. 6 is a graph showing a change with time of vibration acceleration of a seat back frame in Example 2. 6 is a graph showing the relationship between frequency and response sensitivity in a seat back frame including Example 2.

An embodiment of the present invention will be described in detail with reference to FIGS. 1 to 3. In the description, the same elements are denoted by the same reference numerals, and redundant description is omitted. In addition, when showing a direction in description, it demonstrates on the basis of the front-back, left-right and up-down of a vehicle.
FIG. 1 is a structural diagram of a seat back frame provided with a vibration reducing structure for a vehicle seat according to the first embodiment, wherein (a) is a front view and (b) is a side view.

The vehicle seat vibration reduction structure 1 according to the first embodiment (hereinafter sometimes simply referred to as “vibration reduction structure 1”) is applied to, for example, a seat back (backrest portion) of a driver's seat of an automobile for driving. This is a device for reducing vibration of the seat. The application of the vibration reduction structure is not limited to the driver's seat, but can be applied to other vehicle seats such as a passenger seat and a rear seat.
Here, as shown in FIG. 1A, the seat back frame 10 to which the vibration reducing structure 1 is attached is a member constituting a skeleton of the seat back (not shown). The upper frame 11 and the upper frame 11 The left frame 12 and the right frame 13 that extend downward from the left and right ends form a substantially gate shape. A headrest 18 is attached to the upper frame 11.

  The seat back frame 10 is configured by joining a steel pipe member 14 formed in a portal shape and a pair of plate-like members 15 and 15 formed by press-forming a steel plate. The upper end portions 15 a and 15 a of the pair of plate-like members 15 and 15 are fixed to the left and right leg portions 14 a and 14 a of the pipe member 14 by welding. As shown in FIG. 1 (b), the lower end portions 15b and 15b of the pair of plate-like members 15 and 15 are formed wider than the upper end portions 15a and 15a in the front-rear direction. Further, through holes 15c and 15c are provided in the lower end portions 15b and 15b of the pair of plate-like members 15 and 15, and the through holes 15c and 15c are pivotally supported to be tiltable to the left and right end portions of the reclining shaft 16. Has been. Thereby, the seat back frame 10 can tilt forward and backward with the reclining shaft 16 as a fulcrum.

  As shown in FIGS. 1A and 1B, the vibration reduction structure 1 is fixed to the seatback frame 10 and the swinging member 2 that is swingably supported by the upper frame 11 of the seatback frame 10. A sliding member 3 that slides on the swinging member 2 to generate friction, and a pressing mechanism 4 that is fixed to the seat back frame 10 and presses the swinging member 2 toward the sliding member 3. , Is composed of.

The swing member 2 is a member that swings like a pendulum when vibration is input to the vehicle seat. The rocking member 2 has a plate-like plate portion 21 that is elongated in the vertical direction, and a mass portion 22 attached to the lower end side of the plate portion 21.
In FIG. 1A, the state in which the swing member 2 swings left and right is depicted by a two-dot chain line.

  The plate portion 21 has a support portion 21a formed of a through hole on the upper end side. The support portion 21a is swingably supported by a pin 11a projecting from the upper frame 11. The plate portion 21 is slid with a sliding member 3 described later on the rear surface on the lower end side. Although the material of the plate part 21 is not specifically limited, For example, a metal or resin plate can be used.

  The mass portion 22 is a member that functions as a weight of the pendulum, and has a larger mass than the plate portion 21. The mass portion 22 is attached to the front surface on the lower end side of the plate portion 21 with an adhesive or the like. The material of the mass portion 22 is not particularly limited, but can be reduced in size by using a material having a relatively large specific gravity such as lead.

  The sliding member 3 is a member that generates friction by sliding with the swing member 2. The sliding member 3 is provided in the horizontal part between the left frame 12 and the right frame 13 in the horizontal direction, and is provided substantially at the center of the beam part 31 and is formed wider than the beam part 31. And a sliding portion 32. As shown in FIG. 1B, the sliding member 3 is disposed on the rear side with respect to the swing member 2, and the front surface of the sliding portion 32 abuts on the rear surface of the plate portion 21. Is configured.

Here, since the sliding member 3 is installed on the rear side of the swinging member 2, when the occupant sits on the vehicle seat and the seat back tilts backward, the swinging member 2 is moved by the gravity. To generate friction.
Note that at least one of the front surface of the sliding portion 32 and the rear surface of the swinging member 2 is roughened by, for example, sandblasting so that friction is easily generated.

  The pressing mechanism 4 is a member having a function of adjusting the friction by pressing the swing member 2 against the sliding member 3. The pressing mechanism 4 includes a pair of leg portions 41, 41 extending forward from the left frame 12 and the right frame 13, a connecting portion 42 spanned between the pair of leg portions 41, 41, and a connecting portion 42. And a coil spring 43 provided between the swing member 2.

The connecting portion 42 is a member that receives a reaction force in which the coil spring 43 presses the swinging member 2 toward the sliding member 3, is on the front side of the swinging member 2, and includes the support portion 21 a, the mass portion 22, and the like. It is arranged between.
The coil spring 43 is installed in a compressed state between the connecting portion 42 and the swing member 2, and presses the swing member 2 toward the sliding member 3. The coil spring 43 is configured to be detachable, and the pressing force can be adjusted by replacing the coil spring 43. The end of the coil spring 43 on the swing member 2 side is in sliding contact with the swing member 2 in a low friction state so that the swing motion of the swing member 2 is not hindered.
Note that another elastic member such as a leaf spring may be used instead of the coil spring 43.

  The vibration reduction structure 1 according to the first embodiment is basically configured as described above. Next, the operational effects of the vibration reduction structure 1 will be described with reference to FIGS. 1 to 3.

2A and 2B are graphs showing changes in vibration acceleration with time in the seat back frame. FIG. 2A is a comparative example 1 in which no vibration reduction structure is provided, and FIG. 2B is an example in which friction of the vibration reduction structure is appropriately adjusted. 1 and (c) show a comparative example 2 in which the friction of the vibration reducing structure is stronger than that of the first embodiment.
As shown in FIG. 2, the first measurement point P1 is set on the upper frame 11, the second measurement point P2 is set on the mass portion 22 (see FIG. 1), and vibration is input to the seat back frame 10, The vibration acceleration (cm / sec ² ) at the first measurement point P1 and the second measurement point P2 was measured.
The friction of the vibration reduction structure 1 was determined by replacing the coil spring 43 of the pressing mechanism 4 and repeating the experiment while gradually changing the spring force, thereby obtaining an appropriate spring force and friction.

In Comparative Example 1, a predetermined vibration is input to the seat back frame 10 in which the vibration reducing structure 1 is not installed, and as shown in FIG. 2A, the vibration acceleration G (cm / sec) at the first measurement point P1. The time-dependent change of ² ) was measured. As a result, it can be seen that the vibration at the first measurement point P1 continues with substantially constant amplitude and period.

  Next, in the first embodiment, as shown in FIG. 1, the vibration reducing structure 1 is attached to the seat back frame 10, and the spring force of the coil spring 43 of the pressing mechanism 4 is adjusted to adjust the swing member 2 and the sliding member. 3 was adjusted appropriately, the same vibration as in Comparative Example 1 was input, and measurement was performed at the first measurement point P1 and the second measurement point P2.

  As a result, as shown in FIG. 2B, the vibrations at the first measurement point P1 and the second measurement point P2 are out of phase by a predetermined time from the start of vibration. Due to this phase shift, the oscillating member 2 and the sliding member 3 slide to generate friction between them, and vibration energy is consumed (absorbed) by this frictional resistance, and the subsequent vibration acceleration G is attenuated. .

  On the other hand, in Comparative Example 2, measurement was performed by setting the spring force of the coil spring 43 to be stronger than that in Example 1. As a result, the vibration at the first measurement point P1 and the second measurement point P2 hardly caused a phase shift as shown in FIG. Therefore, almost no friction is generated between the swinging member 2 and the sliding member 3, and the damping effect of vibration energy is reduced.

FIG. 3 is a graph showing the relationship between frequency and response sensitivity in the seat back frame.
As shown in FIG. 3, the frequency of vibration input to the seat back frame 10 was changed within a predetermined range, and the response sensitivity (hammering) of the seat back frame 10 at that time was measured.

As a result, when compared with the peak value of response sensitivity, Example 1 in which the friction of the vibration reduction structure was appropriately adjusted was the smallest, and Comparative Example 1 without the vibration reduction structure 1 was the largest. Further, in Comparative Example 2 in which the friction of the vibration reducing structure was stronger than that in Example 1, the peak value was smaller than that in Comparative Example 1, but the peak value was larger than that in Example 1.
Further, when comparing Comparative Example 1 and Example 1, the response sensitivity of Example 1 is lower than that of Comparative Example 1 in the frequency range larger than the peak value of Example 1. I understand that.

  As a result, the vibration reduction structure 1 is provided in the seat back frame 10 and the friction (pressing force) between the swinging member 2 and the sliding member 3 is appropriately adjusted to thereby reduce the vibration of the vehicle seat other than the specific frequency. It can be seen that it can be reduced.

  As described above, according to the vibration reduction structure 1 according to the first embodiment, the swinging member 2 that is swingably supported by the seatback frame 10 and the swinging member 2 that is fixed to the seatback frame 10 and slides on the swinging member 2. And the sliding member 3 that generates friction, the swinging member 2 that is swingably supported by the seatback frame 10 when the vibration is input to the seatback frame 10 is attached to the seatback frame 10. It swings relative to the fixed sliding member 3. As a result, the rocking member 2 and the sliding member 3 slide to generate friction between them, and vibration energy is absorbed. Thus, even if vibrations other than a specific frequency are input and the seat back frame 10 (that is, the vehicle seat) vibrates, the vibrations can be suppressed (attenuated) by friction.

  In addition, according to the vibration reduction structure 1 according to the first embodiment, the pressing mechanism 4 that presses the swing member 2 against the slide member 3 is provided, so that the pressing force between the swing member 2 and the slide member 3 is provided. By appropriately setting the above, it is possible to prevent the swinging member 2 and the sliding member 3 from vibrating in the same phase, reliably generate friction, and appropriately absorb the vibration.

  Further, according to the vibration reduction structure 1 according to the first embodiment, since the swing member 2 is installed on the occupant side with respect to the slide member 3 (in other words, the slide member 3 is provided with the swing member 3). Since the seat back frame 10 is inclined rearward, the swinging member 2 presses the sliding member 3 by gravity. As a result, the pressing mechanism 4 can be simplified and miniaturized, and the pressing mechanism 4 can be omitted when the pressing force by gravity is sufficient (when appropriate).

  Moreover, according to the vibration reduction structure 1 according to the first embodiment, the pressing mechanism 4 is disposed at a position closer to the support portion 21a than the sliding member 3, and therefore, the swinging member at the contact portion of the pressing mechanism 4 2 swing width becomes smaller. For this reason, the pressing mechanism 4 can be reduced in size and weight in accordance with the swing width.

Next, a vibration reduction structure 1A according to the second embodiment will be described with reference to FIGS. In addition, the same code | symbol is attached | subjected about the element same as 1st Embodiment, and the overlapping description is abbreviate | omitted.
FIG. 4 is a structural diagram of a seat back frame provided with a vehicle seat vibration reducing structure according to the second embodiment, wherein (a) is a front view and (b) is a side view.

  As shown in FIGS. 4A and 4B, the vibration reducing structure 1A according to the second embodiment is such that the plate portion 21A of the oscillating member 2 extends greatly below the sliding member 3. However, this is different from the first embodiment described above. Hereinafter, parts different from the first embodiment will be described in detail.

The plate portion 21 </ b> A of the swing member 2 is configured to be longer than the plate portion 21 (see FIG. 1) of the first embodiment, and the lower half of the plate portion 21 </ b> A is below the sliding member 3. It protrudes. The mass portion 22 is fixed to the lower end portion of the plate portion 21 </ b> A protruding downward from the sliding member 3.
The sliding member 3 slides on the rear surface of the substantially central portion in the vertical direction of the plate portion 21A. The pressing mechanism 4 is disposed between the support portion 21a at the upper end of the plate portion 21A and the sliding member 3.

  Thus, by elongating the plate portion 21A, the distance between the support portion 21a and the mass portion 22 is increased, and the moment (inertia moment) of the swing member 2 is increased. It becomes easy to move, and the phase shift between the swinging member 2 and the sliding member 3 increases. As a result, since the pressing force of the pressing mechanism 4 can be increased, the friction between the swinging member 2 and the sliding member 3 can be increased, and the vibration damping effect can be enhanced.

FIG. 5 is a graph showing a change with time of vibration acceleration of the seat back frame in the second embodiment.
For the vibration reduction structure 1A according to the second embodiment, Example 2 was configured by setting the spring force of the coil spring 43 of the pressing mechanism 4 to be substantially equal to the spring force of the coil spring in Comparative Example 2 described above. For Example 2, as shown in FIG. 4, the third measurement point P3 is set on the upper frame 11, the fourth measurement point P4 is set on the mass portion 22, and vibration is input to the seat back frame 10. The change with time of vibration acceleration G was measured.

  As a result, as shown in FIG. 5, the vibrations at the third measurement point P3 and the fourth measurement point P4 (see FIG. 4A) are in a state where the phase is shifted by a predetermined time from the start of vibration. As can be understood from the comparison with FIG. 2B, the time during which the phase is shifted was longer in Example 2 than in Example 1. Due to this phase shift and a larger spring force than in the first embodiment, a larger friction than that in the first embodiment is generated between the swinging member 2 and the sliding member 3, and the first embodiment (see FIG. 2B). The vibration energy can be absorbed more efficiently and the vibration can be attenuated.

FIG. 6 is a graph showing the relationship between the frequency and the response sensitivity in the seat back frame including the second embodiment.
As shown in FIG. 6, in Example 2, the peak value of response sensitivity was further lowered than in Example 1. In addition, response sensitivity was lower than that of Comparative Example 1 in most of the ranges other than the peak value.

  As described above, according to the vibration reduction structure 1A according to the second embodiment, the interval between the support portion 21a of the swing member 2 and the mass portion 22 is larger than that in the first embodiment. Moment (inertia moment) increases, and the swinging member 2 easily swings, and the phase shift between the swinging member 2 and the sliding member 3 increases. As a result, the pressing force of the pressing mechanism 4 can be increased as compared with the first embodiment, so that the friction between the swinging member 2 and the sliding member 3 can be increased, and the vibration damping effect can be enhanced.

  Moreover, according to the vibration reduction structure 1A according to the second embodiment, the sliding member 3 is disposed at the intermediate portion between the support portion 21a and the mass portion 22, and therefore the portion where the mass portion 22 is disposed ( The sliding member 3 comes into contact with a position having a smaller swinging width than the lower end portion of the plate portion 21A. Therefore, the sliding member 3 can be reduced in size.

  As mentioned above, although embodiment of this invention was described in detail with reference to drawings, this invention is not limited to this, In the range which does not deviate from the main point of invention, it can change suitably.

  For example, in the present embodiment, the pressing mechanism 4 is disposed on the passenger side (front side) of the swing member 2, but the present invention is not limited to this, and for example, the swing member 2, the seat back frame 10, and the like. A tension spring may be arranged between the swing member 2 and the swing member 2 against the sliding member 3.

  Further, when the swinging member 2 is appropriately pressed against the sliding member 3 by gravity by tilting the seat back frame 10 or by installing the vibration reducing structure 1 tilted, the pressing is performed. The structure can be simplified by omitting the mechanism 4.

  Moreover, in this embodiment, although the rocking | swiveling member 2 was comprised by couple | bonding the plate part 21 and the mass part 22 which were comprised by the separate member, for example, the thickness dimension of the one end side of a long board | plate material is enlarged. The swing member 2 may be configured by forming the plate portion 21 and the mass portion 22 with a single member by the above method.

  In the present embodiment, the case where the vibration reducing structures 1 and 1A are applied to the seat back frame 10 has been described. However, the frame member is not limited to the seat back frame 10, and for example, a frame member of a seat cushion (seat The vibration reduction structure 1 of the present invention may be applied to a cushion frame.

DESCRIPTION OF SYMBOLS 1 Vibration reduction structure 2 Oscillation member 21 Plate part 21a Support part 22 Mass part 3 Sliding member 31 Beam part 32 Sliding part 4 Pressing mechanism 41 Leg part 42 Connection part 43 Coil spring 10 Seat back frame 11 Upper frame 12 Left frame 13 Right frame 14 Pipe member 15 Plate member 16 Reclining shaft 18 Headrest

Claims (4)

A vibration reduction structure for a vehicle seat,
A swinging member having a support portion swingably supported by the frame member of the vehicle seat;
A sliding member that is fixed to the frame member and slides with the swing member to generate friction;
A vibration reduction structure for a vehicle seat, comprising: The frame member is a seat back frame;
2. The vibration reduction structure for a vehicle seat according to claim 1, wherein the swing member is installed on an occupant side seated on the vehicle seat with respect to the sliding member. The swing member includes a plate portion provided with the support portion on one end side, and a mass portion provided on the other end side of the plate portion and having a mass larger than that of the plate portion,
The vibration reducing structure for a vehicle seat according to claim 1 or 2, wherein the sliding member is disposed between the support portion and the mass portion. A pressing mechanism that presses the swing member toward the sliding member;
The vibration reducing structure for a vehicle seat according to any one of claims 1 to 3, wherein the pressing mechanism is provided between the support portion and the sliding member.

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